Spring winding machine



June 7, 1938. E, w. HALVORSEN ET AL 2,120,146

SPRING WINDING MACHINE Filed Oct. 29, 1957 5 Sheets-Sheet 1 Mm 4 3 S @J 6 6 1 a U W g 5 a m I mw E. n i 2 M; n LL. 7. m i f yam 2% m MW h. J (k I mmm .W a Z w r u u L E. w. HALVORSEN El AL 0,146

SPRING WINDING MACHINE Filed Oct. 29, 1937 5 Sheets-Sheet 2 Jrqaanfms: a/rqrserz (M m June 7, 1938.

June 7, 1938. E. w. HALVORSEN El AL 2,120,146

SPRING WINDING MACHINE Filed Oct. 29, 1957 5 Sheets-Sheet a m g, SLIQI m w: 15' Ina/if fla/mnren Arfkur M'gro June 7, 1938.

E. W. HALVORSEN El AL SPRING WINDING MACHINE- Filed Oct. 29, 1937 5 Sheets-Sheet 4 '...2 78/67/57; Elmer 11/. 7/5 fro/1s 672 1 A I W Ari/z r 6275/? June 7, 1938. E. w. HALVORSEN ET AL 2,120,146

SPRING WINDING MACHINE Filed oct. 29, 1937 s Sheets-Sheet 5 Patented June 7, 1938 UNITED STATES PATENT OFFICE SPRING WINDING MACHINE Application October, 29,

23 Claims.

The present invention relates to spring winding machines of the type adapted to produce what are commonly known as torsion springs, i. e., springs having coiled bodies of different lengths and diameters, with their projecting ends formed or bent to suit various purposes for which the springs may be used.

The object of the present invention is to provide a spring winding machine of the above indicated type, which is characterized by the provision of an improved mechanism for rotatably driving the spindle on which the springs are wound, whereby wide variations in the extent of the winding operation are obtainable, rotation of the spindle being controlled in accordance with a predetermined cycle which provides ample time for severing the wire stock following the winding of a coil and for forming the projecting ends of a spring, as desired. The machine of the present invention further provides for variations in the pitch of the springs produced and an improved mechanism for driving the feed rolls, so that exactly the right amount of wire will be fed past the winding spindle, for one end of the spring about to be wound, without interference with free movement of the stock between the rolls during the winding operation. The machine also provides improved means for severing the wire, for forming its projecting ends and for removing completed springs from the wind ing spindle. The above and other advantageous features of the invention will hereinafter more fully appear from the following description considered in connection with the accompanying drawings, in which:--

Fig. l is a view in side elevation of a spring winding machine embodying the invention.

Fig. 2 is a plan view of the machine shown in Fig. 1.

Fig. 3 is a vertical sectional view, on an enlarged scale, along the line 33 of Fig. 1.

Fig. 4 is a fragmentary sectional view on an enlarged scale, along the line 4-4 of Fig. 1, with associated parts partially in elevation, and partially in section.

Fig. 5 is a horizontal sectional view along the line 5-5 of Fig. 4, looking in the direction of the arrows.

Fig. 6 is a fragmentary view, showing a portion of the parts of Fig. 1 in different positions.

Fig. 7 is a fragmentary sectional view along the line l! of Fig. 2, looking in the direction of the arrows.

Fig. 8 is a fragmentary sectional view along the 1937, Serial No. 171,752

line 8--8 of Fig. 2, with associated parts shown in elevation.

Fig. 9 is a. vertical sectional view along the line 9-9 of Fig. 2, on an enlarged scale.

Fig. 10 is a view in front elevation, on an enlarged scale, of the mechanism for cutting the wire and forming the end of a spring.

Fig. 11 is a vertical sectional view along the line ll-ll of Fig. 10.

Fig. 12 is a fragmentary view in front elevation, showing the mechanism for removing a completed spring from the arbor.

Fig. 13 is a vertical sectional view along theline l3-l3 of Fig. 12, looking in the direction of the arrows.

Fig. 14 is a fragmentary View, illustrating an arrangement of gearing for reversing the direction of the winding spindle.

Like reference characters refer to like the different figures.

Referring first to Figs. 1 and 2, the machine consists of a table I, on which is mounted a spindle head 2 movable on suitable ways 3. A spindle 4 is rotatably mounted in the head 2, and is adapted to be driven by gearing 5, so as to have rotative movement imparted thereto in either direction. A lever 6 is adapted to impart back and forth movement to the head 2 on the Ways 3, the gearing 5 and lever 6 being operable by mechanisms, hereinafter described.

The line of feed for the wire I is indicated by the arrow in Fig. 2, the wire I being fed by rolls 8 through a guide 9 at right angles to the axis of the spindle 4. In the formation of a spring, the wire 1 is first fed between a cylindrical arbor I0 and a pin ll forming part of the spindle 4, see Fig. 3, and subsequent rotation of the spindle 4 causes the wire I to be wound in a coil on the arbor Ill. The length of the spring thus wound is determined by the number of revolutions made by the spindle 4, while the pitch of the spring is determined by the amount of rectilinear movement imparted to the head 2 simultaneously with rotation of the spindle 4.

A spring S is shown as having been wound on the arbor ill in Fig. 10, and after the winding operation, the spring is severed from the wire 1 by means of a tool I! cooperating with the end of the wire guide 9. A second tool l3 cooperates with the tool l2 in order to form the projecting end of the spring just severed, in a manner hereinafter described. The completed spring parts in is then removed from the arbor I0 by a stripping finger l4, after which the spindle 4 is retracted and comes to rest in a position with the space (It) the wire cutting and end forming mechanism,

and (e) the spring stripping mechanism.

Spindle driving mechanism As best shown in Fig. 3, the spindle 4 is rotatably mounted in bearings i6 provided by the head 2. A bolt i6 extending through the spindle 4 cooperates with a threaded opening l1 in a tapered extension I 0a. of the winding arbor ill to lock the arbor in position, so that in effect it forms part of the spindle 4. The outside of the spindle 4 provides elongated teeth I8 in mesh with the teeth of a driving gear l9 mounted on a shaft 20 located below the ways 3, on which the head 2 is moved. Therefore, the spindle 4 and arbor H) are adapted to be rotatably driven simultaneously with rectilinear movement of the spindle head 2.

The shaft 20 carries a pinion 5 forming part of the train of gearing 5 shown in Fig. 1, which terminates in a gear 5" mounted on a shaft 2| below the table I. The shaft 2| carries a pinion 22, which is in mesh with teeth 23a provided at the end of a segment 23 pivotally mounted on a shaft 24 supported by the machine base 25. The segment 23 is adapted to have a back and forth movement imparted thereto from a cam 26 mounted on a drive shaft 21, and the invention contemplates an adjustable driving connection between the segment 23 and the cam 26. By

this connection, the amplitude of movement of the segment 23 can be readily varied to so control the degree of rotation of the winding spindle 4 as to make it possible for the machine operator to very accurately determine the number of convolutions in springs wound on the arbor l0.

As best shown in Figs. 1, 4 and 5, the segment v23 provides a track or raceway 28, which extends at an angle to the pivotal axis of the segment 23, for a purpose which will later appear. The track 28 receives a roll 23 mounted on a stud 30 forming part of an adjusting block 3|, slidable between ways 32 provided by one face of an arm 33, pivotally mounted on a shaft 34 extending beneath the table I. The free end of the arm 33 carries a stud 35, on which is mounted a roll 36 received in the track 26a of cam 26. 'With the parts occupying the position of Fig. 1, it is evident that the roll 36 will be nearest the axis of rotation of the cam 26, and that as the shaft 21 turns through one revolution, the cam roll arm 33 will have an oscillatory movement imparted thereto about its pivot shaft 34.- This movement of the arm 33 will be transformed into oscillatory movement of the segment 23 about its pivot 24 through the operation of the roll 29, and the amplitude of movement of the segment 23 will depend upon the position of the block 3| betwe n the ways 32 on the arm 33.

In order to vary the amplitude of movement of the segment 23, and consequently the number of turns through which the spindle 4 is rotated as the segment 23 swings in one direction, an adjusting screw 31 is provided, by means of which the block 3| may be moved between the ways 32 on the arm 33. The screw 31 is received in a threaded opening 38 extending through the block 3|, and an unthreaded portion 31a at 'one end of the screw is supported in an opening provided in a plate 38 secured at the upper end of the arm 33. The screw 31 is held against longitudinal movement in the plate 39 by means of a collar 40 and a cap 4|, enclosing the end of the screw. The cap 4| provides a squared tool-receiving portion 42, accessible through an opening 43 in the table I, so that the screw 31 can be readily turned to cause shifting of the block 3| on the arm 33, and thereby change the position of the roller 23 in the raceway 28 of the segment 23.

As previously pointed-out, the raceway 28 of the segment 23 extends at an angle to the pivotal I axis of the segment, and the angle is such that the raceway 28 is exactly parallel to the ways 32 of the arm 33 when the parts occupy the position of Fig. 1. In this position, the cam roll 36 is nearest the axis of the cam 26, the segment 23 is at one end of its throw, and the spindle 4 occupies such a position that the space between the-winding pin II and the winding arbor I0 is in exact alinement with the wire guide 3. Consequently, when the screw 31 is turned to cause shifting of the block 3| for the purpose of varying the number of revolutions made by the spindle 4 during one complete revolution of shaft 21, no movement is imparted to the segment 23, and the arbor l0 and pin remain stationary, in readiness for the feeding of wire at the start of the operating'cycle of the machine. As long as the raceway 28 remains parallel to the ways 32, such adjustments can be made at will, and the length of the raceway "is such that the throw of the segment 23 can be varied to cause the winding of springs having from one to thirty convolutions.

Let it now be assumed that the adjusting block 3| has been initially set to produce springs containing an intermediate number of convolutions between the maximum and minimum obtainable, as for example, fifteen, and it is desired to produce springs having one more coil. It is then only necessary to turn the shaft 21 so that the parts occupy the position of Fig. 6, with the cam roll 36 farthest removed from the axis of the shaft 21. The roll 23 on the block 3| has then swung the segment 23 to the left from the position of Fig. l,'so that the winding spindle 4 is at the other extreme of its movement, with a predetermined number of coils wound on the arbor Ill. It is obvious that the raceway 28 is then no longer parallel to the ways 32 on the cam roll arm 33, so that turning of the adjusting screw '31 to shift the block 3| away from the pivotal axis of the segment 23 will actually result in turning the segment 23 farther to the left. Therefore, turning the adjusting screw 31 will have the result of turning the arbor ill, so that the machine operator can actually see another coil formed on the spring, should it be desired to add another turn. When such an adjustment has been made, as for example to increase the number of coils from fifteen to sixteen, continued operation of the machine will result in the pro duction of springs with the desired number of coils, without further adjustment of any other parts. By reason of the above described relation between the raceway 28 on the segment and the ways 32 on the cam roll arm, it is possible to make basic adjustments to wind more or less coils in a spring, without turning the arbor w. and to make minor adjustments to increase the number of coils on a spring already formed, by actually turning the arbor to see that the desired adjustment has been made.

In order to reverse the direction of winding by the arbor it, the gear 5" may be turned around so that itshub will space its teeth from gear 5' on shaft 25, as shown in Fig. 14. A gear 5", with teeth wide enough to mesh with both gears 5' and 5" is then mounted on a stud so as to reverse the rotation of the spindle 3, as compared to Fig. 1.

As previously pointed out, movement of the spindle head 2, accompanied by rotation of the arbor it, will result in the coils of the spring being wound either close together or spaced apart in accordance with the degree of such movement, and there will next be described the mechanism for controlling this movement to accurately determine the pitch of the springs being wound.

Pitch control mechanism As previously pointed out, back and forth movement of the spindle head 2 on the ways 5 is ac complished by means of a pitch lever 5, one end of which is slotted at 54 to embrace a pin 35 carried by a block 55, see Fig. 1. The block 55 is mounted on a screw shaft il, extending between a pair of'spaced lugs 68 provided by the spindle head 2, as best shown in Fig. 2. In setting up the machine, the block 35 is adjusted by turning the screw shaft 5? to determine the initial position of the arbor for the start of the coiling operation. The block is then clamped in the desired position by a bolt 39, which tends to draw together split portions of the block 55 upon the screw shaft 5?. Movement of the spindle head 2 is then entirely dependent upon turning of the lever 5 to control the pitch of the spring being wound.

The opposite end of the pitch lever B is pivotally supported by a stud 50 carried by a bracket 5! overhanging the table I, the length of the lever being such that a relatively small angular turning movement about the pivot 5|) will result in a considerable rectilinear movement of the spin dle head 2 at the free end of the lever. Turning movement is imparted to the lever 5 by means of a roll 52 carried by a stud 53 intermediate the ends of the lever B, the roll 52 being received in a track 56 provided by a pitch cam 55. The pitch cam 55 underlies the lever S, and as best shown in the sectioned portion of Fig. 1, is pivoted at one end on a stud 55 carried by a pitch control slide 5?.

As best shown in Fig. '7, the slide 51 is slidably mounted between ways 58 provided by a slotted base 59, the table I providing a slot 65 through which extends a lug 58, forming part of the slide 51. The lug 5! is connected by a link 82 to the upper end of the segment 23, as shown in Fig. 1, so that oscillatory movement of the segment 23 by the cam 25 is converted into reciprocatory movement of the slide 51. When the pitch cam 55 occupies a position in which the cam track 55 extends at an angle to the Ways 58 for the pitch slide 5?, as shown in Fig. 2, it is evident that movement of the slide 51 to the left, as viewed in Fig. 1, will result in the pitch lever B being turned about its axis to move the spindle head 2 on its ways 3, and so impart a certain degree of pitch to the coils being wound on the arbor I. On movement of the slide 51 to the right of the return swing of the segment 23, the

54, with a'portion Gila-overhanging the end of the cam 55, and spaced therefrom, see Fig. 1. The bracket 63 has a center of curvature about the pivot 55 of the cam 55, and a similarly curved clamping strip 55 fits closely between the overhanging portion Btaand the upper surface of the cam 55. A number of studs 66 are' threaded through the portion 53a andserve to press the strip 55 against the cam 55, and so clamp it in any desired angular position about its pivot 55. Therefore, the cam 55 provides means for imparting the desired pitch to springs being wound on the arbor it, in either direction. Should it be desired to wind 2, fiat spring with its convolutions all lying in the same plane, the cam 55 is clamped in position with the sides of the track 54 in exact parallelism with the ways 58, on which the pitch slide reciprocates.

By reason of the direct connection of the pitch control slide 57 with the segment 23, axialmove ment of the arbor i0 is synchronized with its rotative movement, so that springs will be wound with a uniform pitch for a. given setting of the pitch cam 55. Furthermore, the angular adjustment of the cam 55 about the axis of rotation of the axial roll 52 on the pitch lever 6, provides for a wide range of pitch control. It is also apparent that movement of the roll 52 for a given setting of the cam 55 is substantially multiplied at the free end of the lever B, so that a very small movement of the segment 23 and slide 57 can be translated into a considerably greater axial movement of the arbor Hi to obtain the necessary pitch when winding springs of a very small number of coils.

In the preceding description, reference has been made to the feeding of wire I by the rolls 8 at the start of the spring winding operation, when the arbor occupies the position of Fig." 3, and before the segment 23 is moved by the cam 25 to turn the spindle 4. Any such movement of the feed rolls 8 must be closely timed in the operating cycle, and the mechanism for driving the feed rolls 8 so that they will frictionally engage and feed the wire at just the proper time, will next be described.-

Feed roll mechanism As best shown in Fig. 4, the shaft 27 carrying the cam 25 extends beneath the table I, and carries at its other end a bevel gear 61 in mesh with a bevel gear 68 on a shaft 69 extending upwardly through the table I. The shaft 69 is connected by bevel gears 10 to a cam shaft H extending across the table I at right angles to the drive shaft 2'1, as shown in Fig. 2. The shaft 27 is driven from a suitable source of power, such as an electric motor M, located in the base 25, as shown in Fig. 1. The motor M is connected by belts l2 and pulleys T3 to a shaft 14, connected by gearing E5 to teeth 16 formed on a circular portion of the cam 25. A lever 17, pivoted at 18, provides an operating portion "a, accessible from the front of the machine for turning the lever, and thereby operating a clutching device 19 associated with the pulley 13, as indicated in dotted lines in Fig. 2. Obviously, the shaft 21 carrying the cam 28, could be driven directly from any source of power other than the motor, the main consideration being that the shaft 21 and the cam shaft 1| be so connected that they rotate at the same rate of speed.

As best shown in Figs. 2, 8 and 9, the shaft 1I carries a cam 88, adapted to impart a reciprocatory movement to a slide 8| connected by a link 82 to an arm 83. The arm 83 is pivotally mounted on a stud 84, carried by a bracket 85 surrounding a shaft 88, on which is mounted one of the feed rolls 8. The arm 83 provides a raceway 81 in which is received a roll 88 mounted on a stud 88 forming part of a block 88. The block 88 is slidable between ways 8| extending longitudinally in a segment 82 pivotally mounted on a stud 83. The opposite end of the segment 82 provides teeth 84 in engagement with the teeth of a pinion 85 mounted on the feed roll shaft 88. As best shown in Fig. 9, the shaft 88 also carries a gear 88 in mesh with a gear 81 mounted on a shaft 88 carrying the other feed roll 8. Movement of the segment 82 about its pivot 83 is caused by turning of the arm 83 about its pivot 84 in response to reciprooatory movement of the slide 8| by the cam 88. Such movement of the segment 82 is transformed into rotative movement of the roll shaft 88, and the other roll shaft 88 is turned in unison therewith, in the opposite direction of rotation by the gears 88 and 81.

The degree of rotative movement imparted to the feed rolls 8 depends upon the amplitude of the swinging movement of the segment 82, and such movement is in turn dependent upon the position of the block 88 in the raceway 81. In order to shift the block 88, a screw shaft 88 is received in a threaded opening I88 in the block 88, with an unthreaded portion 88a turnable in a plate I8I at the end of the ways 8|. The shaft 88 is held against axial movement by a collar I82 and an enlarged head I83 providing a squared tool receiving portion I84. By turning the shaft 88, the block 88 can be shifted to vary the throw of the segment 82 for a given amount of turning movement of the arm 83 by the cam 88. Thus, the feeding of wire 1 by the rolls 8 can be closely controlled, so as to determine the length of wire that is fed past the arbor to provide one end portion of the spring that is subsequently wound by rotation of the arbor I8. I

As best shown in Fig. 9, the shaft 88 carrying the left-hand feed roll 8, is mounted in a bracket I85 pivoted at I88, so that the left-hand roll is capable of movement toward or away from the stationary axis of the right-hand roll 8. A spring I81 connected at its ends to the bracket I85 and to a fixed part of the machine, serves to yieldingly maintain the bracket I85 against an adjustable stop I88, so that normally the rolls 8 are not in gripping engagement with the wire 1, and the wire may pass freely therebetween during the winding operation.

In order to cause the rolls 8 to engage the wir with sufilcient pressure for feeding, the shaft 1| carries a cam I88, with which cooperates a roll II8 yieldingly mounted on an arm I I I of the roll bracket I85. The arm carries a sleeve I I2, within which is received a plunger II3, with the roll 8 rotatably mounted at the end of the plunger, which extends through the sleeve II 2. A spring II4 serves to yieldably maintain the plunger 3 in the position shown, wherein the roll II 8 is just out of engagement with the peripheral portion of the cam I88. This normal position of r the roll H8 is determined by the adjustment of the stop I88, cooperating with the bracket I 85. As the shaft 1| rotates, a projection I 88a of the cam I88 engages the roll II8 to force the plunger I I3 inside the sleeve I I2, thereby compressing the spring H4 and tending to turn the bracket I85 about its pivot I88. While the spring I81 resists turning of the roll bracket, the positive force under the cam I88 acting through the compressed spring H4 is sufficient to turn the bracket and cause the left-hand roll 8, as viewed in Fig. 9, to press against the other roll 8 and so grip the wire between.

The cam I88 is so formed and so timed with respect to the cam 88, that the wire 1 is gripped between the rolls 8, just before movement of the slide'8I, acting through the arm 83 and segment 82, imparts rotative movement to the rolls 8. Therefore, when the rolls 8 rotate in unison in opposite directions, indicated by the arrows in Fig. 2, a predetermined length of wire will be fed between the arbor I8 and pin II. The rolls stop as the slide 8| comes to rest, whereupon the roll II8 leaves the cam projection I88a and the roll bracket I85 returns to its original position against the stop I88, with the wire no longer gripped between the rolls. The above described feeding of the wire takes place while the arbor I8 is stationary, since at that time the roll 38 on the arm 33 is received in a dwell on the winding cam 28, as shown in Fig. 1. Thus, the feed of the stock takes place at the start of the winding cycle, and the rolls 8 have released the wire by the time the segment 23 starts to move and thus impart rotative movement to the winding spindle 4. After the wire has passed between the released rolls 8 during the winding operation, the segment 82 is returned by the cam 88 to its'starting position, but the rotation of the non-engaged rolls 8 has no effect on the wire 1, due to the provison of a pair of check rolls II5, which will rotate only in the direction in which the rolls 8 turn for feeding.

As previously pointed out, rotation of the arbor I8 in one direction, results in winding a spring with a, predetermined number of convolutions and of a given pitch, after which the arbor comes to rest, due to another dwell on the winding cam 28. 'While the arbor I8 thus remains stationary, the tool I2 severs the completed spring from the wire where it leaves the guide 8, after which the tools I2 and I3 cooperate to bend the projecting end of the completed spring by mechanism which will next be described.

Wire severing and end forming mechanism As best shown in \Figs. 10 and 11, the wire guide 8 extends through a holder I I8 supported by a bracket II8a, which also provides vertical guideways II1 for a pair of tool slides H8 and H8, mounted above and below the guide 8. The slides provide seats II8a and 811 for receiving springs I28, bearing on a portion of the bracket I I8, so that each slide is yieldingly held away from the guide 8. A lever I2I pivoted at I22 has one end bearing on the upper surface of the slide I I8, while its other end carries a roll I23 yieldingly maintained in engagement with the periphery of a cam I24 by the pressure of the spring I28. A lever I25, pivoted at I28, similarly co-operates with the lower surface of slide II8, with a roll 1| beside the cam I24. I

The lower slide II8 carries the cutting tool I2, while the upper slide II8 carries the forming tool I3, and normally, the tools I2 and I3 remain in the retracted positions of Fig. 11, while a spring S is wound on the arbor I8. in the manner previously described. When the arbor I comes to rest with a spring wound thereon, the wire extends from the arbor I0 into the guide 9, between the tools I2 and I3. Continued rotationof the cam shaft II, with the spring winding and wire feeding instrumentalities at rest, then causes the cams I28 and I24 to move the tools I2 and I3 into the dotted line position of Fig. 11.

As the slides H8 and H3 move toward the wire I, the offset portion of the forming tool I3 engages the wire at a point between the wound spring S and the end of the guide 9, as the upwardly moving cutting edge of the lower tool I2 severs the wire at the guide 9. This severs the spring from the wire stock and continued upward movement of the cutting tool I2 results in the projecting end portion of the spring engaged by the tools being bent around the offset portion of the then stationary forming tool I 3. The cams I24 and I28 then permit the slides H9 and H9 to be moved away from the wire guide 9 by the springs I20, thereby retracting the tools I2 and I3, and leaving a completed spring S on the arbor I0 with one end formed, as indicated. Obviously, other types of cutting and forming tools may be employed, without departing from the invention; for example, the tool slides H8 and H9 may be replaced by a multiple tool forming head surrounding the wire guide 9, such as is shown and described in the 'copending application of Charles R. Bergevin, Serial No. 171,120, filed October 26, 1937. The completed spring is now ready to be moved from the arbor I0 by a stripping mechanism, which will next be described.

Spring strz'pp ing mechanism As best shown in Figs. 12 and 13, the stripping finger I4 is mounted at the end of an arm I29, pivoted at I30 on a slide I3I movable in horizontal ways I32 provided by a bracket I33. The stripper arm I29 provides an extension I34 below the pivot I30, to which is connected one end of an operating link I35, having its other end connected to a lever I36. The lower end of the lever I 36 is pivoted at I31, and a spring I39, connected at its ends to the lever I36 and to the bracket I33, serves to maintain the lever I36 in engagement with a roll I39 on a multiplying lever I40. The lever I40 is pivoted at MI. and carries a roll I42 between the roll I39 and its pivot I4I. The pull of the spring I38 serves to maintain the roll I42 in engagement with a cam I43 mounted on the shaft II.

With the parts occupying the position of Fig. 12, the link I35 exerts a thrust on the extension I34 of the stripper arm I29, so as to turn the arm I29 about its pivot I30, and thereby maintain the stripping finger I4 in a raised position entirely clear of a spring being wound on the arbor Ill. The cam I43 is so timed that after a spring has been wound on the arbor I0 and severed from the wire at the guide 9, a projection I43a engages the roll I42 and turns both levers I40 and I36 to the left, as viewed in Fig. 12. When this occurs, the pull of the link I35 first turns the arm I29 so that it extends substantially parallel to the arbor I0, with the finger I4 engaging the completed spring on the arbor. An adjustable stop I44 carried by the slide I3 I limits turning movement of the arm I29, so that after the arm I29 engages the stop I44, further movement of the link I35 by the lever I36, results in movement of the slide I3I to the left. This causes quick removal of the completed spring from the arbor I0 by the stripping finger I4, even though movement of the spring is accompanied by movement of the arbor I0 in the same direction, as the spindle head 2 is moved to return the pin II to the position which it occupies at the start of the winding operation.

Operation and adjustment of the machine Having described the various mechanisms entering into the machine, its operating cycle will be briefly described,- with reference to the form of the cam 26 of Fig. 1. Assuming that the cam roll 36 occupies the position shown the arbor I0 is then at rest, with the space between the winding pin I I and the arbor I0 exactly in line with wire guide 9; Rotation of the drive shaft 21, and with it the cam shaft 'II,'then causes the rolls 8 to immediately grip the then stationary wire, and feed a predetermined length of wire past the arbor. The arbor remains at rest during this feeding, due to the dwell on the cam 26, at the start of the cycle. After the wire has been fed, turning of the segment 23 serves to rotate the arbor I0, accompanied by rectilinear movement of the spindle head 2, thereby winding a spring on the arbor, having a predetermined number of convolutions and a given pitch. These operations occur while the segment 23 moves from the position of Fig. 1 to the position of Fig. 6.

At the end of the winding operation, the arbor I0 comes to rest, due to a second dwell on the cam 29, whereupon the cams I24 and I20 operate the tools I2 and I3 to cause the wire to be severed at the guide 9, and to cause the end of the spring to be formed. After the severance of a completed spring, the segment 23 moves in the opposite direction, thereby returning the spindle head 2 to its original position, and turning the arbor I0 in the opposite direction to the starting position, reversal of the arbor I0 being accompanied by operation of the stripping finger I4 to remove the completed spring from the arbor III. This completes the operating cycle, leaving the parts in position for. the commencement of another cycle.

As previously pointed out, the number of convolutions wound in a spring can be varied through a Wide range, by turning the screw 31 to shift the block 3I, with the parts occupying the position of Fig. 1, wherein the raceway 28 is parallel to the ways 32. If, after winding springs having a given number of convolutions it is desired to increase the length of thesprings,

such adjustment can be quickly made by moving the parts to the position of Fig. 6, wherein turning of the screw 31 will result in convolutions being added to the spring already wound, within the view of the machine operator. Variations in the pitch of the springs being wound are readily obtained by adjusting the angle of the pitch cam 55, with respect to the line of movement of the slide 51. In order to vary the amount of wire fed by the rolls 8, to provide for one end of the spring that is to be wound, the

' screw shaft 99 is turned to shift the block 90.

ment thereto and causing said arbor to make a predetermined number of revolutions in either direction of rotation for each revolution of said drive shaft.

2. In a machine of the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor, a pivoted arm actuated by said cam and an adjustable connection between said arm and gear member for imparting a predetermined degree of oscillatory movement to said gear member.

3. In a machine of the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor, a pivoted arm actuated by said cam, a connection between said arm and gear member for imparting oscillatory movement to said gear member and means for adjusting said connection to cause said arbor to make a predetermined number of revolutions in either direction of rotation for each revolution of said cam.

4. In a machine of the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor, a pivoted arm actuated by said cam, a connection between said arm and said gear member for imparting oscillatory movement to said gear member and means operable without moving said arbor for adjusting said connection to vary the humber of revolutions made by said arbor for one revolution of said cam.

5. In a machine of the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor, a pivoted arm actuated by said earn, a connection between said arm and said gear member for imparting oscillatory movement to said gear member and means operable in one position of said cam for adjusting said connection to vary the number of revolutions made by said arbor for one revolution of said cam, said adjustment being accomplished without imparting rotative movement to said arbor.

6. In a machine of the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor providing a guideway, a pivoted arm actuated by said cam also providing a guideway, a.connection between said arm and gear member movable in both guideways and means for adjusting said connection to vary the number of revolutions made by said arbor for a given throw imparted to said arm by said cam.

'7. In a machine of, the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor providing a guideway, a pivoted arm actuated by said cam also providing a guideway, a connection between said arm and gear member movable in both guideways and means for adjusting said connection to vary the number of revolutions made by said arbor for a given throw imparted to said arm by said cam, adjustment of said connection, when said guideways are in parallel relation and said arm is nearest the axis of rotation of said cam, being obtainable in the absence of angular movement of said arbor.

8. In a machine of the class described a rotatable winding arbor, a drive shaft carrying a cam, a gear member for rotating said arbor providing a guideway, a pivoted arm actuated by said cam also providing a guideway, a connection between said arm and gear member movable in both ,rotatably mounted on said'head, a drive shaft,

guideways and means for adjusting said connection to vary the number of revolutions made by said arbor for a given throw imparted to said arm by said cam, adjustment of said connection, when said guideways are non-parallel and when said arm is farthest from the axis of rotation of said cam, serving to also impart angular .m'ovement to said arbor.

9. In a machine of the class described, a frame, a head movable on said frame, a winding arbor a gear member for rotating said arbor, a connection between said drive shaft and said gear member for imparting a predetermined degree of oscillatory movement to said gear member, a lever for imparting rectilinear movement to said arbor head and a connection between said gear member and said lever, whereby axial movement is imparted to said arbor simultaneously with its rotative movement.

10. In a machine of the class described, a frame, a head movable on said frame, a winding arbor rotatably mounted on said head, a drive shaft, a gear member for rotating said arbor, a connection between said drive shaft and said gear member for imparting a predetermined degree of oscillatory movement to said gear member, a lever for imparting rectilinear movement to said arbor head and an adjustable connection between said gear member and said arbor head actuating lever for controlling the amount of movement imparted to said arbor head for a predetermined degree of rotative movement imparted to said arbor by the movement of said gear member.

11. In a machine of the class described, a frame, a head movable on said frame, a winding arbor rotatably mounted on said head, a drive shaft, a gear member for rotating said arbor, a connection between said drive shaft and said gear member for imparting a predetermined degree of oscillatory movement to said gear member, a lever for imparting rectilinear movement to said arbor head, a reciprocatory slide connected to said gear member and an adjustable connection between said slide and said arbor head actuating lever to control the degree of pivotal movement of said lever for a given amount of movement of said slide by said gear member.

12. In a machine of the class described, a frame, a head movable on said frame, a winding arbor rotatably mounted on said head, a drive shaft. a gear member for rotating said arbor, a connection between said drive shaft and said gear member for imparting a predetermined degree of oscillatory movement to said gear member, a lever for imparting rectilinear movement to said arbor head, a reciprocatory slide connected to said gear member, a track angularly adjustable on said slide and a connection between said arbor head actuating lever and saidtrack for converting movement of said slide into pivotal movement of said lever to an extent determined by the setting of said track.

13. In a machine of the class described, a frame, a head movable on said frame, a winding arbor rotatably mounted on said head, a drive shaft, a gear member for rotating said arbor, a connection between said drive shaft and said gear member for imparting a predetermined degree of oscillatory movement to said gear member, a

' lever for imparting rectilinear movement to said arbor head, a reciprocatory slide connected to said gear member and a connection between said slide and said arbor head actuating lever located nearer the pivotal axis of said lever than the point of connection of said lever to said head.

14, In a machine of the class described, a frame, a head movable on said frame, a winding arbor rotatably mounted on said head, a drive shaft, a gear member for rotating said arbor, a

connection between said drive shaft and said gear member for imparting a predetermined degree of oscillatory movement to said gear member, a lever for imparting rectilinear movement to said arbor head, a, connection between said gear member and said arbor head actuating lever for converting oscillatory movement of said gear member into rectilinear movement of said head and an adjustable connection between said head and said lever to determine the initial position of said head and arbor.

15. In a machine of the class described, a winding arbor, means for imparting intermittent rotative movement to said arbor, a pair of rolls for receiving stock extending in the direction of said arbor, a gear member for imparting rotative movement to said rolls, a pivoted arm for imparting oscillatory movement to said gear member and an adjustable connection between said arm and said gear member for controlling the amount of stock fed past said arbor by rotation of said rolls.

16. In a machine of the class described, a pair of rotatably mounted rolls, one of which is yieldingly supported to permit stock to pass freely between said rolls, means for imparting rotative movement to the other of said rolls, means for causing the first-named roll to frictionally engage said stock prior to rotative movement of the other roll in one direction of rotation to cause feeding of said stock and means for releasing said first-named roll from the stock in advance of rotative movement of the other roll in the opposite direction of rotation.

17. In a machine of the class described, a pair of rotatably mounted rolls, one of which is yieldingly supported to permit'stock to pass freely between said rolls, means for imparting rotative movement to the other of said rolls, means for causing the first-named roll to friotionally engage said stock prior to rotative movement of the other roll in one direction of rotation to cause feeding of said stock, means for releasing said first-named roll from the stock in advance of rotative movement of the other roll in the opposite direction of rotation and means for checking, movement of the stock in a direction opposite to its movement of feeding. g

18. In a machine of the class described, a rotatable winding arbor, means for feeding stock past said-arbor when the latter is stationary, means for imparting rotative movement to said arbor for winding a length of stock thereon in the form of a spring, said feeding means being displaced from the winding axis with a straight length of stock extending from a spring wound on said arbor, tools operable in a vertical plane at right angles to the line of stock feed and means for operating said tools after a spring has been wound on said arbor to sever said straight length of stock and bend the end of the spring still on said arbor.

iii. In a machine of the class described, a rotatable winding arbor, means for feeding stock past said arbor when the latter is stationary,

means for imparting rotative movement to said arbor for winding a length of stock thereon in the form of a spring, said feeding means being displaced from the winding axis with a straight length of stock extending from a spring wound on said arbor, tools operable in a vertical plane at right angles to the line of stock feed and means for operating said tools after a spring has been wound on said arbor to cause one tool to first engage said straight length of stock and then cause the other tool to sever said stock andbend the free end of the spring still on said arbor aroun said first tool.

20. In a'machine of the class described, a rotatable winding arbor, means for feeding stock past said arbor, means for rotating said arbor to wind said stock thereon in the form of a spring, means for severing a spring from said stock, a stripper normally maintained out of engagement with a spring on said arbor and means for imparting a combined pivotal and rectilinear movement to said stripper to engage a spring on said arbor and remove it therefrom.

21. In a machine of the class described, a rotatable winding arbor, means for feeding stock past said arbor, means for rotating said arbor to wind said stock thereon in the form of a spring, means for severing a spring from said stock, a stripper normally maintained out of engagement with a spring on said arbor, means for first imparting a-pivotal movement to said stripper to engage it with the end of a spring on said arbor and means for next imparting a longitudinal movement to said stripper to cause it to remove said spring from the arbor.

22. In a machine of the class described, a winding arbor, a pair of rolls for receiving stock extending in the direction of said arbor, means for imparting intermittent rotative movement to said arbor, in one direction, to cause it to wind said stock into a coil, means for imparting intermittent rotative movement to said rolls to feed said stock past said arbor in the intervals between success sive stock winding movements thereof, and means for varying the degree of rotative movement of said rolls to control the amount of stock fed past said arbor by rotation of said rolls.

23. In a machine of the class described, awinding arbor, a pair of rolls for receiving stock extending in the direction of said arbor, said rolls being normally free of said stock, means for imparting intermittent rotative movement to said arbor, in one direction, to cause it to wind said stuck into a coil, means for frictionally engaging said rolls with said stock and rotating said rolls to feed a length of stock past said arbor when the latter is stationary, and means for varying the degree of rotative movement of said rolls to control the amount of stock fed past said arbor by rotation of said rolls.

mm W. HALVORBIN'. ll

ARTHUR C. MORO- 

